Kerf-cutting machine



De@ 14, 1943. g, A, LINDGREN 2,336,992

KERF- CUTTING MAQHINE Filed Jan. 2, l1941 4 sheets-sheet 1 Q W f mwN-ron ,o Fran@ Ling/gwen @kuma/lk TTORNEY Dec. 14, 1943. F. A. LINDGREN 2,336,992

KERF-CUTTING MACHINE Filed Jan. 2, 1941 4 Sheets-Shea# 2 WN n v gwmwmdp.

u vi nv ATTGRNEY Dec. 14, 1943. A [NDGREN 2,336,992

KERF-CUTTING MACHINE Filed Jan. 1941` 4 sheets-sheet 3 fig. 4

gang/, Lin/@Ken ATTORNEY Dec. 14, 1943. F. A. LINDGREN KERF-CUTTINGv MACHINE n m .W www wfw T mL. m Ar Patented Dec. 14, 1943 UNITED STATES j TENT ortica KERF-CUTTING MACHINE Frank A. Lindgren, Western Springs, ll., assignor to Goodman Manufacturing Company, Chicago, Ill., a corporation of Illinois e Claims.

This invention relates to improvements in kerf-cutting machines of the room and pillar type.

One of the objects of the invention is to provide an improved feeding mechanism for machines of the character described, including a fluid coupling of the hydrokinetic type, so as to afford a more compact gearing arrangement for the machine as a whole, while providing greater iiexibility and ease of control in the driving connections between the electric motor and the feed cable. A further object is to provide a fluid coupling connection between the electric motor and the drive coupling for the truck, used for transporting the korf-cutting machine from place to place in the mine.

A still further object of the invention is to provide an improved and simplified form of retarding device to take the place of a separate tail rope cable and drum heretofore commonly employed on kerf-outting machines. For this purpose, I provide a fluid operated braking mechanism adapted to engage the ground adjacent the rear end of the machine, and adjustable longitudinally of the machine so as to counterbalance the pulling effect of the feed rope while the machine is being fed laterally along the mine wall for cutting.

Other objects of the invention will appear from time to time as the following description proceeds.

The invention may best be understood by reference to the accomanying drawings, in which Figure l is a fragmentary plan view of a mining machine constructed in accordance with my invention, with parts broken away to show interior details thereof;

- Figure 2 is a side elevation of the machine shown in Figure 1, mounted in transporting position on a truck, with parts broken away to show certain gearing details;

Figure 3 is an enlarged detail section taken on line 3 3 of Figure 1;

Figure 4 is a detail section drawn to a still larger scale than Figure 3, taken on line d t of Figure 1;

Figure 5 is a plan viewI of the planetary gear mechanism, showing details of the gear shifting mechanism in section;

Figure 6 is a longitudinal section taken generally on line 5 5 of Figure l;

Figure 7 is a fragmentary plan View showing the rear end of the machine and its driving connections with its truck when mounted on the latter as shown in Figure 2;

Figure 8 is a detail section taken .generally on line 3 3 of Figure 1, showing details of the retarding device, and showing the latter in raised or retracted position;

Figure 9 is a transverse detail section of the retarding device, showing the latter in lowered or extended position;

Figure 10 is a plan view showing the mining machine in different angular positions relative to the working face of the mine while cutting, and illustrating the operation of the retarding device under varying conditions.

Referring now to details of the machine shown in the drawings, the invention is shown as applied to a room and pillar machine including a Y wheels 38, 39.

and mounted as usual to extend from the front end of the machine frame I2 between a base plate I3 and an electric motor I4. The base plate I3 with side walls I5, I5 forms a cuttings discharge passage extending beneath the motor IQ and a gear casing It at the rear end of the machine. The cutter chain extends about a driving sprocket Il on upright shaft I8 having suitable bearing in the gear casing I6. The electric motor I4 has suitable driving connection with the sprocket shaft I, as by a pinion I9 on motor armature shaft 2d meshing with a gear 2! on longitudinal shaft 22 having suitable bearing in the gear casing I6. A bevel gear 23 on shaft 22 meshes with a bevel gear 24 having a hub 25 loosely mounted on the sprocket shaft I8 as by anti-friction bearings 26, 21 (see Fig-v ure 6). A sliding clutch member 2B of suitable form is mounted on hub 25 and has jaw teeth 29 adapted to engage a ring 3d xed on the sprocket shaft. With the gearing arrangement described, the cutter chain can be declutched or clutched at will to be driven directly from the electric motor in the usual manner.

The machine is adapted to be transported from one cutting place to another on a truck indicated generally at 32 in Figures 2 and 7. Said truck has a platform 33 with guide rails 34, 34 at opposite sides mounted on a base frame 35 having front and rear axles B, 31 with supporting The truck is designed to be driven from the electric motor I of the mining machine through a coupling mechanism indicated generally at d0, supported at the rear end of the base frame 35 of said truck and adapted to be detachably coupled to the motor I4, as will hereinafter more fully appear.

Referring now more particularly to the flexible.

feed mechanism and its fluid coupling connection with the electric motor, which constitute one of the novel features of my invention, a feed rope drum 42 having a rope or cable 43 wound thereon is mounted as usual at one side of the machine so that the rope can either be trained forwardly chine, for maneuvering the machine over the" mine floor or drawing it upon the mine truck, as.

required.

In the form of feed rope drumfmounting shown herein, the drum 42 is loosely mounted on a 'hub 48 of an internal gear member 49 which in turn is rotatable on a stud 50 mounted on and projecting outwardly from the side lof gear casing" I6.'

Saiddrurn 42 can be clutched at will to the gear member 49 by a suitable clutch, herein consisting` of a pin 5I ofthe usual form, carried bythe drum and Iadapted to be engaged inany one of a series`of holes 52, 52formed in the face of said internal gear member. Thepin 5l .is operated as usual byahandle'53.

The internal'geari member 4.9 is driven by a pinion 54 on shaft 55 extending through the gear casing ljiand having a worm gear 56 thereon meshing with worm 51 on longitudinal shaft 58'. The worm and worm'gear just` mentioned arev preferably of the self-locking type, so that the drum 42 can be held 'against unwinding by pull on the rope 43, forpurposesV that will hereinafter is connected toa fluid coupling of the hydrokinetic type indicated generally at 60, havingits impeller driven by the motor aty approximately the relatively high'speed of the latter. J

The'gear reduction device 59herein shown consists *of-a two speed planetary of a general typef heretofore commonly employed in kerf-cutting machines, including a sun gear 6I keyed on shaft, 62 leading fromv the fluid coupling and meshed with a planetary gear 63 on shaft 64 (see Figuresl 4 and 5). A second planetary gear 65 of slightly larger pitch` diameter is rotatable with said planetary gear 63 on shaft 64. The latter shaft is mounted at opposite ends in rings 66, S6 forming part of a cage 10, as will presently appear.

As is usual with planetary devices of the type herein employed, two or three similar sets of planetary gears 63 and 65 may be provided,rbut only one such set need be shown and described herein. `TIheplanetaries 63 and 65`are meshed respectively with internal gears 61 and 68, rotatable independently of each other. The internal gear 68 has a hub 69 keyed on shaft 58.. Y

The cage 10 has a shell V1|V surrounding the internal gear 68, a hub portion 12 rotatable on the hub 69 of said internal'gear, and an inner frame member 13 (see Figure 5) Vof which the end rings 66, llrforxnV a part. The peripheral portion 14 of the internal gear 61 has bearing in a recess 15 formed inthe adjacent margin of cage 10.

vThe shell11! of cage 10and Aadjacent periphery 14- of .internal gear 51 have 'external gear teeth J6-and 11, respectively, of equal pitch diameter extending-thereabout and adapted to be selectivelyA engaged `by a toothed stop block 18 on shifter rod 19 so as to restrain rotation of cage 10 Vor, internalrgear.61.Y The shifter rod 19 is mounted inbrackets 19a, 19a for manualoperation in any suitable manner.

It will now be observed that when the cage 10 is held against rotation, shaft 64 with planetary gears 63 and 65 are likewise held against rotation about the sun gear, but said planetaries are free to rotate on their own axes to advance the internal gear 68 at relatively low speed. On the `other hand, when the internal gear 61 is held against rotation, the planetary gears 63 and 65 rotate with the cage 10, and advance the internal gear 68 at relatively high speeed. The shift- 1 ing of stop block 18 from gear teeth 18 on the outer shell of cage 10 to gear teeth 11 on the outer periphery of the gear 61, or vice versa, provides van instantaneous, positive change in gear ratio in the planetary. VThe form'of fluid coupling 60 herein shown is of the scoop controlled type heretofore used in the application of power to various kinds of machinery. This scoop type of coupling affords certain advantages, principally that ofY manual control, in its present application to a kerf-cutting machine, but it will be understood that many of the advantages of a fluid coupling can be obtained by other well known types s uch as pump filling, or traction (constant filling) couplings, or variations thereof. y

The uid coupling shown herein consists primarily of an impeller 8|, runner 82, and enclosed cover or casing 83, rotating with the impeller. The impeller is keyed to shaft which is driven by motor I4 through gear 86, idler gear 81 and gear 2l on the longitudinal drive shaft 22. The last named gear is driven by the armature pinion I9, previously described in connection lwith the cutter chain drive gearing. The runner 82 is keyed to shaft 62 leading to the planetary gear device 59. Rotation of the impeller 8| at high speed causes the usual circulation of oil between vanes 8|a and 82a formed in the opposed faces of the impeller andrunner, respectively.

The amount of oil in the working circuit to vary the output speed or completely declutch the unit, is controlled by the adjustable scoop tube 88. Said tube is mounted eccentrically at one end of the casing 83 and is pivoted so it can be swung into and out of the annular ring of oil held by centrifugal force against the outer rim of said casing. When the scoop tip is in its outermost position as shown in'Figure 4, it picks up the oil in the outer casing and carries it through cored openings 89 in a manifold 90 and into the working circuit inside of an inner casing 9| and between the Vimpeller and runner, to transmit maximum power. i v

When the scoop isset in retracted position (shown in dotted lines in Figure 3) itis out of the annular ring of casing oil and carries no oil to the Workingvcircuit. Leak-off nozzles 92 around the rimrof the inner casing 9| allow a constant escape of oil from the working circuitto the outer casing, and as no replacing oil is received from the scoop tube when in retracted position, the working circuit will be emptied and further power transmission will cease.

Adjustment of the scoop tube in intermediate positions determines the amount of oil in the working circuit and varies the resulting output speed and power. y

The scoop tube 88 is preferably of the two way type, that is to say, it has two ducts at the end thereof, with their tips facing in opposite directions, so as to be operable in either direction of rotation of the fluid coupling. The scoop tube is adjusted as usual by a lever arm 84 having a toothed segment 93 thereon which may be manually operated by a control shaft 94 having a pinion 94a meshed with said segment.

The shaft 53 which drives the feed drum ft2 from the duid coupling and planetary gear as hereinbefore described, is also extended through the rear end of the gear casing i6 and has a socket member S5 thereon for detachable driving connection with the coupling mechanism El of the truck 3'2, as shown in Figures 2 and 7.

The truck coupling mechanism is comprises a coupler rod 9S having an irregular shaped head 91 adapted to t in the socket 95 on 'drive shaft 58, and also having a squared rear end portion 91a slidably mounted in bevel gear 98. Said bevel gear is supported in the front wall of gear housing 99 carried upright on bracket idd. The bevel gear 98 is meshed With bevel gear ll keyed on transverse shaft H32. The latter shaft has a chain sprocket |03 at its outer end, about which a drive chain Idd is trained. The drive chain extends downwardly under a pair of idlers H35, it and thence forwardly about a drive sprocket lill on the rear aXle 31.

The transverse shaft may also have a friction brake band |68 of the usual kind thereon, for use "f when the truck is being propelled along the mine tracks.

The coupler rod 96 is held in coupling position by a yoke Il!) det'achably engaged at opposite ends to the rear wall of the gear housing 9S by pins I l l, and having 'a centrally disposed bearing member H2 adapted to engage an enlargement H3 on the rear end of said coupler rod. The arrangement is such that the yoke il@ can be disl cutting machines, and in addition to the low i starting torque and flexibility of drive which are characteristic features of a iluid coupling.

It will be understood that in ordinary cutting operations the cutter bar is fed to the coal at a predetermined speed suitable for average cutting conditions, but from time to time unusually hard cutting conditions are encountered, voften while making a single cross cut. A fluid coupling in the feed drive, as herein disclosed, provides an automatic slip or reduction in torque transmitted ,A

to the feed drum so as to reduce the feeding speed, without reducing the torque transmitted from the motor directly to the cutter chain. In fact, since the torque transmitted to the feed drum may be substantially reduced, due to the slowing down of the motor under unusually hard cutting conditions, the power available for transmission to the cutter chain will be correspondingly increased. Thus the cutter chain can usually work its way through hard places at temporarily reduced feeding speed, and the machine will immediately resume its normal feeding speed as soon as cutting conditions are again normal, with no attention from the operator.

It will be observed that the fluid coupling operates to provide the desired slip or speed reduction above set forth, with much greater uniforme ity, and without the loss of power that is incident to slip friction devices of the kind heretofore employed in korf-cutting feed mechanism. A fluid coupling can be depended upon to provide a predetermined gradual change in slip corresponding to its loperating speeds, whereas with ordinary slip friction devices it is usually necessary `to build up the torque to a relatively high slipping point, whereupon it will suddenly become released. Moreover, in such devices, the amount of torque to promote slippage, and the amount of slippage finally resulting, is always more or less variable and unpredictable.

Another advantage of the feed gearing arrangement herein disclosed is greater compactness especially in vertical dimensions, that is made possible by the use of the fluid coupling. Probably the most efficient and compact form of reduction gearing heretofore used for feed gearing is a two speed planetary gear device with a slipfriction control on one or both speeds. The friction control is usually by band brakes, to protect the gearing from excessive strains or shocks as well as to vary the speed of drive. Such friction controlled planetary gear is usually disposed near the end of the feed drum gear train and must be of substantial overall diameter in order to afford the required gear reduction and peripheral friction braking surface.

It will be observed that the use of the fluid coupling eliminates the necessity of friction bands or the like on the planetary gear reduction, in the form shown herein, high and low speed members 61 and 10 being positively engaged by the stop block 18, so as to produce an instantaneous change in gear ratio, instead of being frictionally controlled, as heretofore, by brake bands. In this way, the change in gear ratio can be accomplished much more readily and positively than in prior machines in which it takes an appreciable amount of time, as well as skill and energy, to adjust the friction bands manually to the proper tension.

It will also be observed that owing to the selflocking worm and worin gear disposed between the planetary gear and the feed drum 42, as herein disclosed, the feed drum will be held from unwinding while the planetary is being shifted from one speed to the other. This feature is especially desirable when the machine is being dragged over sloping ground, and it is undesirable to loosen the rope i3 relative to its anchor while changing speeds. Moreover, with the fluid coupling interposed between the planetary and the motor, the change in speed can be quickly made without stopping the motor, simply by declutching the coupling temporarily.

Referring now to the novel form of retarding device, a depressible brake member i i5 is mounted at one side of the machine opposite the feed drum 42 in position to be extended into and out of engagement with the ground.k In the form shown, said brake member comprises an elongated metal shoe Mii cooperating with a superimposed casing lll to form a generally cylindrical housing for a fluid expansible chamber H8 of rubber or similar flexible material. Studs or bosses Illia on the bottom face of the shoe will increase its retarding effect.

The casing Il'l is rigidly mount-ed on a plate H9 which is slidably supported between a pair of guides E28, l2! disposed along the side wall l5 of the cuttings discharge passage, as clearly shown), and having threaded engagement in an ear |24 integral with the casing ||'|.A The shoe H6 is guided for vertical movement relative to the casing vby a pair 'of longitudinally disposed pins |26 carried at the inner side of the casing, and engaging inV slots |21 at'the adjacent side of the shoe (see Figure 9). The shoe ||6 also has suitable retracting means, herein consistingof tension springs |28, |28 connected between the shoe and casing at each end ofthe device, as shown in Figure 8. Y l

Fluid is introduced into theexpansible chamber I8 by a pipe |3|, leading through a boss|32 which is slidably engagedin` a slot |33 extending longitudinally of the-housing IB, as shown in Figures 8 and 9. 4 Y

Fluid pressure is supplied to the chamber from a hydraulic pump '|35 of any suitable form which herein is shown as` being continuously driven by the electric motor througha pinion |36 on drive shaft 22. The high pressure pipe 31 leads from the motor to aithree way control valve |38, and from thence, pipe |3| goes tothe expansible chamber, and a second pipe |39 goes Vt0 tank |40. A relief valve IM is also connected directly between pipe |31 and tank |40. ,The Vlow pressure side of the pump is connectedto the tank |40 by pipe |42. The arrangement issuch that by opening valve |38 to pipe |3| the pressure in chamber||8 will expand the latter downwardly and depress the shoe H into braking engagement with the ground. By throwing the control valve |38 in ,a second or inoperative position, the pump will be unloaded through pipe |39 to the tank. In said inoperative position the pipe |3| also has connection through pipe |39 tothe tank to relieve the chamber H3V of operating pressure. Y

The retarding device above described is used in place of the tail rope drum and tail rope connections heretofore generally employed with kerfcutting machines of the room and pillar type.

A typical example of its method of use is illustrated diagrammatically in Figure 10. As usual,

the machine is shown as cutting from right to left'with the feed rope 43 anchored to a xed abutment and Vextended from sheave Mat the front left corner of the machine along the Working face F so as to pull the machine laterally with its longitudinal axis disposed substantially at a right angle to'said working face. Heretofore, such machines have had a retarding rope or cable adapted to be trained from the rear right corner of the machine, and paid out at such retarding speed as to counterbalance the pull on the sheave 44 and thus maintain the machine at the proper angle to the working face. As is well known, the amount of retardation required varies under different conditions, and at different times, depending upon the length of the cutter bar, the hardness and speed of cutting, the frictional resistance of the base plate of the machine itself, and other factors. `I find, however, that under ordinary lcutting conditions, the desired retardation can be provided by my novel braking device, its degree of effectiveness being controlled by shifting the shoe longitudinally of the machine to the point where the machine is maintained at the proper cutting angle. Thus, as seen in Figure 10, if the machine in moving from position A to B assumes the angle shown in position B, this is due to insufcient retardation of the rear end of the machine. This condition is readily corrected by moving the retarding device rearwardly, to a position as shown in position C, so that the machine will again assume its proper cutting angle to the working face. Thus the retarding device is entirely self-contained and eliminates the setting of an additional jack for the tail rope, and the delays incident to the manipulation of the tail rope itself.

While I have herein shown and described one formY in which my invention may be embodied, it will be understood that the construction thereof and the arrangement of the various parts may l be altered without departing from the spirit and scope thereof. Furthermore, I do not wish to be construed as limiting my invention to the specic embodiment illustrated, excepting as it may be limited in the appended claims.

I claim as my invention:

1. In combination in a korf-cutting machine, a motor, a chain-carrying cutter bar, a sprocket for said chain, and positive geared connections between said motor and said chain sprocket, flexible feeding means for said cutter bar including a winding member, a hydrokinetic iluid coupling driven by said motor, a plural speed gear mechanism driven by said iiuid coupling have positive change speed means, and self-locking worm gears driven by said gear reduction mechanism, and operatively connected to said winding member to y hold the same from unwinding while said gear shift means is being operated to change the speed ratio of said gear mechanism.

2. In combination in a. kerf-cutting machine,a motor, a chain-carrying cutter bar, a sprocket for said chain, and positive geared connections between said motor and said chain sprocket, flexible feeding means for said cutter bar-including a winding member, a hydrokinetic uid coupling driven by said motor independently of said chain sprocket drive having manually controllable means for varying the torque transmitted thereby from zero to maximum at working speeds of said motor, and gear reduction mechanism between said iiuid coupling and said winding member including a plural speed planetary gear having positive change speed means.

3. In combination in a kerf-cutting machine, a motor, a chain-carrying cutter bar, a sprocket for said chain, and positive'geared connections between said motor and said chain sprocket, flexible feeding means for said cutter bar including a winding member, a hydrokinetic fluid coupling driven by said motor independentlyof .said chain sprocket drive, a plural speed planetary gear device driven directly from said fluid coupling and opeartively connected with said winding drum, said planetary gear device including two rotatable reaction members having positive selective stop means therefor, and operative con-4 nections between said planetary gear and said winding drum including self-locking worin gears, to hold said winding drums for unwinding while said positive stop means is being operated to change the ratio of said planetary gear device.

4. In combination in a kerry-cutting machine, a frame, a motor on said frame, flexible feeding means including a winding drum, a truck for transporting-said Keri-cutting machine having drive coupling means thereon, a common drive member on said frame for said winding drum and FRANK A. LINDGREN. 

